Junked metal compressing smasher

ABSTRACT

A JUNKED METAL COMPRESSING SMASHER COMPRISES A BASE OR ANVIL BOXED IN BY SAID WALLS AND AN END STOP AT REAR END AND WITH A CANTILEVERED PLATFORM AT FORWARD END. THE HAMMER IS SUPPORTED ABOVE THE BASE BY SUPPORT ARMS AT A TRANSVERSE STATION PIVOTALLY CONNECTING BASE AND FORWARD END OF HAMMER, AND BY SUPPORT ARMS OF EQUAL LENGTH BETWEEN PIVOT CONNECTIONS, AT A TRANSVERSE STATION REARWARDLY OF THE FIRST STATION, PIVOTALLY CONNECTING SAID BASE AND SAID HAMMER AT EQUAL DISTANCE ON SAID HAMMER AS THE DISTANCE BETWEEN BASE STATIONS. THUS, BY THIS PANTAGRAPH TYPE CONNECTION ARRANGEMENT THE CRUSHING FACE OF THE HAMMER CONTINUOUSLY REMAINS SUBSTANTIALLY IN A HORI-   ZONTAL PLANE AS IT DESCENDS. MEANS COOPERATIVE WITH HOIST CABLE DEAD ENDED ON THE HAMMER AND HOIST RESPECTIVELY EFFECT THE RETURN OF THE HAMMER TO A RELEASABLY LATCHED UPWARD POSITION AFTER EACH DESCENT TO CRUSH JUNKED METAL.

NOV. 1971 w. D. BALLARD JUNKED METAL COMPRESSING SMASHER 5 Sheets-Sheet 1 Filed July 11, 1969 511? 0. BALLIJRD INVENTOR. ZJA ELM ATTUFNE Y 5 Sheets-Sheet 2 INVENTOR W 8, W

W. D. BALLARD JUNKED METAL COMPRESSING SMASHER WESLEY D BALM/e0 Nov. 30, 1971 Filed July 11. 1969 ATTORNEY Nu @m 1971 w. D. BALLARD JUNKED METAL COMPRESSING SMASHER Filed July 11, 1969 D. BALLARD WESLE Y INVENTOR ATTORNEY N v- 3 7 w. D. BALLARD 3,923,425

JUNKED METAL COMPRESSING SMASHER Filed July 11, 1969 5 Sheets-Sheet 5 A T TOENE Y "United States Patent 9 3,623,425 JUNKED METAL COMPRESSING SMASHER Wesley D. Ballard, 2809 W. Garfield St., Phoenix, Ariz. 85009 Continuation-impart of application Ser. No. 780,625,

Dec. 3, 1959, which is a continuation-in-part of application Ser. No. 555,187, June 3, 1966, now Patent No. 3,413,914, dated Dec. 3, 1968. This application July 11, 1969, Ser. No. 840,902

int. Cl. B30 7/00 11.5. Cl. 100233 11 Claims ABSTRACT OF THE DISCLOSURE A junked metal compressing smasher comprises a base or anvil boxed in by said walls and an end stop at rear end and with a cantilevered platform at forward end. The hammer is supported above the base by support arms at a transverse station pivotally connecting base and forward end of hammer, and by support arms of equal length between pivot connections, at a transverse station rearwardly of the first station, pivotally connecting said base and said hammer at equal distances on said hammer as the distance between base stations. Thus, by this pantagraph type connection arrangement the crushing face of the hammer continuously remains substantially in a horizontal plane as it descends. Means cooperative with hoist cable dead ended on the hammer and hoist respectively effect the return of the hammer to a releasably latched upward position after each descent to crush junked metal.

This application is a continuation-in-part of application Ser. No. 780,625, filed Dec. 3, 1969, now abandoned. Application Ser. No. 780,625 was a continuation-in-part application of application Ser. No. 555,187, filed June 3, 1966, and which issued as Pat. No. 3,413,914 on Dec. 3, 1968. Both applications related to a machine for compressing junked metal, as automobile bodies, by letting fall thereon a heavy weight or hammer which is continuously cable connected to the means which lets it descend substantially freely and then raises it.

Application Ser. Nos. 851,254, filed Aug. 19, 1969, and 21,092, filed Mar. 19, 1970 also relate to a junked metal compressing smasher.

The objects of the invention, as stated in the parent application, are repeated herewith.

It is consequently a primary object of this invention to provide a junked metal compressing smasher of this class which is adapted to compress metallic objects, as metallic chassis and frame parts, into more compact or reduced sizes for more economic hauling.

It is also another object of this invention to provide a machine of this class which is preferably portable so that it may be taken to the location of junked metal at remote locations from larger types of metal compacting and processing machinery.

It is a further object of this invention to provide a smasher of this class which includes a heavy hammer that is hinged at one end and adapted to be power lifted and gravity lowered to smash an object, as a junked automobile on a bed or base from which the hammer is pivoted, the base providing side walls and a rear end to upstand from the bed to form a die or restraining form, thus limiting the spread of the crushed metal.

It is also an important object of this invention to provide a smasher of this class with bed side walls providing openings therein and means to insure the easy disposition of the lifts of fork lift trucks with relation to the bed or base in handling uncrushed bodies onto, and compressed bodies from off, the base.

It is also another and important object of the invention 3,623,425 Patented Nov. 30, 1971 to provide a smasher of this class with a bed adapted to hold a plurality of smashed car bodies that is within the load carrying capacity of the particular fork lift truck that is available for feeding bodies to the smasher.

It is still another object of the invention to provide a smasher of this class which may be handled from a truck and tandem wheels onto the ground into smashing position, and back onto a truck and tandem wheels for transportation, in manner that only a pair of jacks is necessary in handling.

It is yet a further object of the invention to provide a metal body crushing machine or smasher of this type which is constructed in manner to require limited head room in transportation so that it may pass under underpasses, overhead bridges, and the like without difiiculty.

It is also a further object of the invention to provide a smasher of this type which has a heavily weighted hammer designed to be raised rapidly to be freed to descend by gravity with inappreciable friction and great smashing impact.

The part of the invention that pertains to the part added by the immediately preceding continuation-in-part application has all objects hereinabove recited for the parent application as such are applicable to the disclosure added herein, and has additional objects as follows:

As a primary object the invention by the preceding continuation-impart application provides a junked metal compressing smasher which presents a substantially horizontally disposed crushing contact surface as it descends and smashes metal, the hammer remaining in constant connection with the hammer lift means.

It is also another and further object of this invention to provide a junked metal compressing smasher of the class described immediately hereinabove, which includes a cooperative means in association with hammer lift and cable, that automatically returns the hammer to detachably latched, raised position, after each smashing descent.

It is still another object of the invention to provide a smasher of this class which provides a lost motion member in the brake lever setting rod disposed between hammer, upon return to upper position, and the brake lever aforesaid, thus to provide against part breakage upon hammer over-travel.

Also, it is another important object of the invention to provide a smasher of this class which is automatically returned to upper, brake applied, declutched position, by limit switch and solenoid operation.

It is still a further important object of the invention to provide a smasher of this class which is automatically returned to upper, brake applied, declutched and safety latched operation by cable actuation of mechanical means to effect clutch engagement.

Furthermore, it is an important object of the invention to provide a smasher of this class which interposes manual operation to release brake and raise safety latch to initiate each descent of the hammer to crushing position.

Other and further objects will be apparent when the specification herein is considered in connection with the drawings, in which:

FIG. 1 is a side elevational view of a smasher comprising an embodiment of the invention with front end pivotally connected to the fifth wheel on the end of a trailer, or behind a truck or prime mover, the rear end being supported on a tandem wheel unit;

FIG. 2 is an isometric view of a smasher as shown in FIG. 1, the machine being shown in operating position ready to crush a second automobile body on top of a first body that has already been crushed as restrained to predetermined spread by the bed of the machine; the position shown also being the position of hammer disposition when the jacks are applied to reload the smasher on trailer and tandem;

FIG. 3 is a small scale side elevational view, showing the machine disclosed in FIGS. 1 and 2 with hammer in the second position for reloading;

FIG. 4 is a small scale side elevational view of the machine shown in FIG. 3, with hammer in the third position of reloading;

FIG. 5 is a small scale side elevational view of the machine shown in FIG. 3 with hammer in the fourth or last position of reloading;

'FIG. 6 is a plan view of the smashes shown in FIGS. 1, 2 and 3;

FIG. 7 is a fragmentary, isometric view of the smasher shown in FIGS. 1, 2, 3 and 6;

FIG. 8 is a fragmentary, transverse elevational view, part in section, looking rearwardly at the station of the hammer pivot shaft, as taken along line 88 of FIG. 6.

FIG. 9 is a side elevational view of another embodiment of the invention;

FIG. 10 is a fragmentary plan view, part in section, taken along line 10-10 of FIG. 9;

FIG. 11 is a fragmentary isometric view of a front end portion of a hammer, as shown in side elevation in FIG. 9;

FIG. 12 is a fragmentary side elevational view, part in section, showing hammer parts in descent, or nearing high impact;

FIG. 13 is a fragmentary plan view, partially diagrammatic, as seen looking down upon the forward portion of the machine including the forward portion of the hammer in lowered position;

FIG. 14 is a fragmentary side elevational view, showing disposition of pivot arms, as taken along line 14-14 of FIG. 13;

FIG. 15 is a fragmentary side elevational view of the platform with winch having lifted hammer to uppermost position to contact switch that de-clutches hoist drive and applies brake;

FIG. 16 is a diagrammatical view of solenoid operation of clutch and brake levers;

FIG. 17 is an isometric view of an embodiment of the invention comprising the part added as new by this appli cation; such isometric view being for the purpose of showing brake and clutch lever positions with relation to prime mover, transmission, reel, drum, and brake band;

FIG. 18 is an elevational view of platform with clutch engaging and dis-engaging mechanism thereon, shown partially diagrammatically, with clutch lever in clutch disengaged position; winch turning in free-wheeling condition, as hammer descends;

FIG. 19 is an elevational view of platform with clutch engaged and hoist or winch just beginning to lift the hammer; clutch lever accordingly having been urged rearwardly;

FIG. 20 is an elevational view of platform with brake applying and releasing mechanism thereon, shown partially diagrammatically, with brake lever having been moved by hammer urged brake rod to brake applied position; safety lock being shown locking hammer in upwardly locked position, release pedal for starting a new cycle also being shown; and

'FIG. 21 is a large scale sectional elevational view showing spring urged, lost motion arrangement for brake setting rod contraction to release brake while hammer arm is still upright.

Referring now in detail to the drawings to the drawings of the continuing part of the application, in which like reference numerals are applied to like elements in the various views, a junked metal compressing smasher or crushing machine 10 is shown in detail in FIGS. 1-2, and in FIGS. 68, with the machine comprising essentially a base 11 and a hammer 12 pivotally mounted on a pivot shaft 13 journalled at either end in brackets 14a, 14b connected to the base 11.

At its forward end the base 11 includes a forward cantilever construction 15 which includes a strong upright part 16 upstanding from the forward end of the base 11 and an operators platform 17, cantilevered forwardly therefrom to provide a support for the operational mechanism 18 and to rest, in transit, as on the rear end of a truck bed or trailer 19, and centrally over a fifth wheel construction 20 carried on the rear end 19, so that a pivot bolt 21 may be installed downwardly, centrally through the platform 17 and through the conventional socket or bore provided therefor in the fifth wheel, thus to provide a vertical pivotal connection between the crusher or smasher 10 and the truck bed or trailer 19 of the prime mover which pulls the smasher.

At its rear end the base 11 includes a rearward cantilever construction 22 with a strong upright part 23 upstanding from the rear end of the base 11 and a horizontally extending cantilevered part 24 to the rear thereof having a downwardly opening angle box or rectangular extension frame 25. A tandem unit or assembly 27 of two pair of traction wheels has an upper part comprising a rectangular boss 26 which is received or fitted into the angle frame 25 beneath the cantilever part 24 whereby the rear part of the crusher 10 is supported in transit. Additionally, bolts, not shown, may bolt the rear cantilever part of the tandem unit 27.

The central portion of the base 11 or the base proper 11a, is comprised of longitudinal members in the form of sturdy structural shapes, as inwardly facing channels 2 8 outermost, with I-beams 29 transversely spaced apart centrally thereinbetween, these beams or shapes being connected forwardly to the rear of the forward upright 16 and rearwardly to the rearward upright 23. As best shown in FIG. 8, these structural members are tied together by a lower base plate 30 to which they are welded. Also they are tied together by, and welded upwardly to, an upper base 31 which extends over the beams, from just to rear of the hammer pivot to the rear cantilever construction 22.

Additionally at the forward end of the base central portion 11a, the beams 28 and 29 are floored by a top plate 31a forwardly of the hammer pivot. Also, on each side, forwardly, smaller, outwardly facing channels 32 are provided to extend rearwardly and to support on each side the respective brackets 14a, 14b in which are journalled the ends of the hammer pivot shaft 13. Between its respective ends the pivot shaft 13 passes through a succession of spaced apart upright legs or members of the hammer 12, the outer legs 33a being connected upwardly to the respective outer, longitudinally extending, structural members or inwardly facing channels or hammer runner members 34.

Between the outer legs 33a, spaced apart central or inner legs 33b are connected upwardly to a transversely extending structural or hammer plate 3 5 which extends from channel 34 on one side to channel 34 on the other side. Also, the pivot shaft 13 is supported by longitudinally extending, smaller channels 36, which are disposed between the I-beams 29, and between the I-beams 29 and outer structural members or channels 28, and which extend rearwardly from the forward cantilever upright 16, and which are welded to and supported upon, the lower base plate 30.

The forward and rear ends of the hammer are tied together, between the ends of the channels 3 1, by structural plates or angles 37, and spaced inwardly of the outer beams or runner channels 3 the hammer 12 includes 1- beams 38, with a larger, central I-beam 39 being spaced centrally between the I-beams 38. Also, longitudinally spaced apart cross-connecting members 3711 are provided between the beams as transverse elements. It should be noted that the hammer, for weight, may be constructed of other and heavier shapes, to meet performance requirements, and also the base 11 can be constructed of various heavy shapes and forms to withstand the pounding imposed upon it in service.

In order to restrain the automobile bodies crushed upon the base 11 substantially to predetermined plan areas and thicknesses, respective side walls or upright side members 40a, 40b are provided to extend along the base 11 on either side thereof, the walls being comprised of respective forward, central and rear sections 41a, 41b, 410, respectively, with each section comprised of upright beams 42, longitudinally extending runners or upper and central connecting members 43a, 43b, and a longitudinally extending beam, channel or lower runner 44 extending between the uprights 42 for the length of the side wall sections. The inner surfaces of the side walls, which form the die or restraining elements channelizing the spread of junked metal when a car body is crushed, comprise forward, central and rear plates 45a, 45b, 45c.

Vertically extending slots 46a, 46b are thus provided between the respective wall sections 41a, 41b and 41b, 410 which are slightly greater in width than the width of the forks or fingers of the conventional fork-lift truck lifts, as will be hereinbelow described, the slots extending from the tops of the walls downwardly to the tops of the respective runners 44.

Also, in connection with the operation of the fork lift trucks which handle the positioning upon, and removal of the automobile bodies from, the base plate 31, a pair of pipe or half-pipe sections 47 are welded to the top plate 31 of the base 12, which extend outwardly from the respective slots 46a, 46b over the plate 31, as indicated in FIG. 2, and in dotted lines in FIG. 6.

At the forward end of each side wall forward section 41a, a triangularly shaped gusset or forward brace 48 is provided, comprised of a triangularly shaped plate 49 and a diagonally extending structural member, as a channel 50, the bases of the gussets 48 being connected to, and supported upon the respective side channels 32. Also, crossconnecting beams, bars, or brace elements 51 are connected forwardly to the respective rear top corners of the cantilever upright 16 and rearwardly to the top of the respective gussets 48 and forward corners of the forward side wall sections 41a.

The hammer 12 is lifted and lowered by a cable 52, one end of the cable being dead-ended on the reel drum of a winch 53 mounted on the rear portion of the forward cantilever platform 17. From the drum 53 the cable extends under a sheave of a double sheave pulley 54 mounted at the top of an A-frame 55 which upstands from the central portion of the hammer 12. In detail the A-frame 55 comprises opposed, transverse structural channels 56 which extend diagonally upwardly from their connections to the hammer side runners 34, to an apex in the form of the housing and mount 57 for the pulley 54, such mount 57 being best shown in FIGS. 2 and 6, but being omitted for purposes of clarity in FIG. 1. The A- frame is completed by a forward diagonally extending I-beam 58 from the central longitudinal beam 39 of the hammer to the apex 57, and by a rearward diagonally ex tending I-beam 59, from the I-beam 39 to the apex 57, the brace member 59 being in turn braced by a diagonally extending member 60, as indicated in FIG. 1.

The cable 52 extends upwardly around the rear part of the first sheave of the pulley 54 and forwardly and downwardly around the forward part of the first sheave of a double sheave pulley 61 which is mounted in a bracket assembly 86 carried centrally on top of the top transverse member 62 of a frame 63 which upstands centrally above the cantilever platform 17. Thence the cable 52 extends rearwardly and under and around the rear part of the second sheave of the A-frame pulley 54, and over the back forwardly over the second sheave of the forward pulley 61, and downwardly around the forward part of such second sheave, to terminate functionally in a clamp 64 which is mounted upon a cross-brace or cross-tie 65, spaced under and parallel with the transverse member 62, and thus between the two forward uprights 66 of the frame 63.

The frame 63 additionally includes two spaced apart, longitudinally extending runners 67 between the tops of the forward uprights 66 and the tops of the rear uprights 68 which upstand from the rear part of the platform 17; a transverse member 87 tying together the tops of the rear uprights 66, and the transverse member 62 tying together the forward uprights 68, as aforesaid. Also, the frame 63 may include adequate conventional crossbracing, or diagonally extending members, not shown, in order to provide clarity of disclosure for the parts shown. The cable 52 extends downwardly from the clamp 64, which dead-ends it to the frame 63, and around a reserve drum 69 which is supported by, and has its shaft journalled in, brackets 70 which are mounted on the forward part of the platform 17.

Since the frame 63 functionally dead-ends the forward end of the cable 52, its component structural elements should be of substantial strength, and in effect the frame 63 comprises a truss. To this end, diagonally extending brace members 71 extend downwardly from the top elements at the rear of the frame 63, through slots 72 in the hammer 12, and are affixed to the top surface of the upper plate 31 of the base portion 11a, thus to strengthen the base longitudinally.

A gasoline engine 73 is mounted on the platform 17 to drive the winch 53 which pays out and takes up the cable 52, the engine shaft 74 having a pulley 75 mounted thereon to drive, through conventional sprocket chain or belting, a pulley 76 on one end of a jack-shaft 77 which is journalled in, and supported by conventional pillow blocks mounted on the platform 17 to the rear of the engine 73. A pinion 78 is mounted on the other end of the jack-shaft 77 to mesh with a large gear 79 on the end of the winch shaft 80, the winch shaft 80 being properly journalled in, and supported by, brackets 81 which upstand from the platform 17. A conventional transmission guard 86 is provided for the pulleys 75, 76, as shown in FIG. 7, and a corresponding guard, not shown, may be provided for the gear 79 and pinion 7-8.

The operators position on the platform 17 is determined by the location of the operating levers 8-2, 83, which are shown mounted on the platform 17, more or less diagrammatically, to indicate that the operators post must be laterally outwardly from the engine shaft 74, the levers being operatively connected by connection means 84, also indicated diagrammatically in FIG. 7, to select direction of Winch rotation (to take up or pay out cable) and to clutch-connect the engine shaft 74 to be driven. Thus, the lever 82, through connection means 84, may operate clutch means, as within the frusto-conical engine housing part 85, to connect the engine shaft 74 to drive the winch 53, and the lever 83, by its position, disposes the connection means 84 in manner to determine direction of winch drum rotation. The dotted line arrow thus indicates that the winch drum.53 has rotated in counter-clockwise direction to raise the hammer 12.

A strong pipe is shown in the drawings extending transversely across the hammer 12 near the forward end thereof, the pipe 90 being afiixed to the structural members 34, 38, 39 as by welding. Also, in FIG. 2, two opposed jacks 88a, 88b, indicated diagrammatically as hydraulic jacks, are shown as being provided with transversely extending support arms or bars 89, from the tops or heads of the jacks 88a, 88b, such supports being of diameter to be slid into the socket providing ends of the pipe 90 when the hammer 12 is raised to position the axis of the pipe 90 in co-axial alignment with the support bar axis when the jacks have been manipulated to raise the support bars to a predetermined level.

If the cable 52 is now freed, by manipulation of the levers 82, 83 on the platform 17, whereby the hammer 12 may descend by its own weight, downwardl from the position shown in FIG. 2, the rearward end of the machine 10 may be scraped slightly forwardly along the ground as the forward end of the machine 10 pivots upwardly about the support and pipe axis into the air, as shown in FIG. 3.

In this position the rear end cantilever 22 is too low to receive a tandem unit 27 thereunder as a first step in transferring the machine from ground to wheeled support. Also, in relationships of hammer pivot 13 with pivot ipe 90 on machines, the hammer 12 could be raised high enough to lift the jacks 88a, 881) off the ground sufficiently to let the machine base 1110: return to sit flat upon the ground, the same as shown in FIG. 2, thereby making no progress.

However, if, as shown in FIG. 4, a block or log 92 is placed under the base 11a, a predetermined distance to the rear of the transverse plane of the jacks 88a, 88b, and parallel thereto, the hammer 12 might then be raised to such a height to lift the jacks 88a, 88b from the ground a very slight distance, whereby the forward upper corner of the block 9-2 becomes the fulcrum, and the forward corner of the cantilever upright 16 moves to the ground as the rear end of the machine 10, including the cantilever 22 is carried upwardly into the air.

The raising of the hammer 12 to the position shown in FIG. 4 has taken the load off of the jacks 88a, 8812, as aforesaid, but when the hammer is lowered again, the jacks seat again and the load is transferred from the block 92 to the jacks and as the hammer is further lowered the forward end of the machine 10 moves upwardly about the fulcrum of pipe 90 and support bars 89 therein, and the rear end of the machine '10 moves downwardly. As this takes place the tandem unit 27 is wheeled beneath the rear cantilever section 22 and manipulated, so that as the frame 25 descends, the aforesaid described rectangularly cross-sectioned boss or tandem unit upper frame part 26 is received within the frame part 25 on the under side of the cantilever member 24. Thus, as shown in FIG. 5, the rear end of the machine 10 now bears on the rear portion of the tandem unit upper part 26, while the hammer 12 has been fully lowered to rest on the rear part of the base 11a, the forward end of the machine 10 still being raised amply above the rear part of a trailer or prime mover 19 which is being backed under such forward end.

At this stage the hydraulic fluid pressure lifting the upper parts of the jacks 88a, 88b may be released to let the upper parts of the jacks descend, and consequently the forward end of the machine 10 may descend as the rear end 19 of the truck is maneuvered to place its fifth wheel 20 in position to have the fifth wheel connection member 21 installed through the platform 17 to connect the prime mover 19 and machine 10, whereby the machine 10, by the use of the hammer 12 in cooperation With the jacks 88a, 88b, has rapidly been transferred from ground support to wheeled support. It should well be appreciated that the adaptability of the machine 10, which has to be quite heavy to function as intended, to be changed from operative ground support to wheeled support for transport to further locations of junked metal bodies, can provide a highly competitive advantage to an operator of such a machine as will be further emphasized in detail hereinbelow.

The invention is designed to solve at least one economic problem; that of inexpensively transferring junked automobile bodies from out-of-the-way locations, or smaller lots, as found in smaller sized cities, to large cities Where economy permits the provision of means whereby automobile bodies may be further processed to be handled in reduced bulk, as in compressed bales, or shredded metal bundles, on the route of junked metal to steel mill furnaces.

The provision of side Walls to complete a bed, permits a plurality of bodies to be handled, one after another being crushed to the height of the bed, to make a load to the capacity of a fork-lift truck load. Thus, the quickly crushed loads may be handled from the bed of the machine and loaded to the capacity of a truck bed, or truck load capacity, so that several fork-lift truck loads can be carried in one hauling truck load, to the site of a massive shredder or baling press, or directly to the site of a steel mill furnace.

An embodiment of the invention introduced by the immediately preceding continuation-impart application is shown in FIGS. 9-16 disclosing a crushing or junked metal smashing machine comprising a base 101 including an anvil or junked metal supporting box bottom 102 of structural shape and plate construction. From the forward end of the box bottom 102 a cantilever construction 103 extends forwardly to provide a platform 104 on which is mounted the hammer lift apparatus 105 from which extends the cable 106 to the hammer 107 shown mounted by forward and rear pivot arms 108, 109 which dis-pose the hammer 107 with smashing or crushing under surface 110 above the box bottom 102. Any stop wall 111 may extend across the foot of the box bottom 102 to define the rearward spread of the crushed or junked metal, thus to bound the rear face of the bundle or bale resulting from the fall of the hammer 107. As shown in FIGS. 9 and 10, the stop wall 111 is provided as the front wall of a rearwardly cantilevered section 112, for the same purpose as such section shown in the foregoing forms of invention first disclosed in the parent application, and useful in the unloading and reloading of the smasher 100, when hauled to location by a prime mover.

Sidewalls 113, 114 upstand from the sides of the anvil or box bottom 102, each being comprised from forward end, rearwardly, of successive uprights 115a, 115b, 1150 as angles, above the floor 116 of the box bottom 102, and mounting a runner, as an angle 117a; successive uprights 1181:, 118b, mounting a runner 1171); and successive uprights 119a, 119b mounting a runner 1170, all as best indicated in FIG. 9.

The rear pivot arms 109, on either side of the hammer 107, have their lower ends pivotally mounted on pivot pins 120 which extend transversely outwardly from the sides of the box bottom 102. The upper ends of these arms 109, are pivotally connected to pivot pins 121 which extend transversely outwardly from the side of an upper hammer section 107a which is spaced above the lower hammer section 107b on each side by forward uprights 122a; intermediate uprights 122b, 1220, 122d; rear uprights 1222, and diagonally extending rear toe members 122 Runners 123 on the opposed sides of the upper hammer section 107a have rack teeth 123a along the upper rear surfaces thereof into which may fit teeth 124a on a rack 125 on each side of the underside of a counterweight 126 which extends across the upper hammer section 107a. Thus, by selectively moving the counterweight 126 forwardly or rearwardly upon the upper hammer section runners 123 the center of the mass of crushing contact of the hammer 107 may be adjusted in accordance with the center of the mass of a junked metal body, as an automobile to be crushed. For instance, such a shift might be made prior to crushing a series of junked automobile bodies of the same make known to have a center of mass at a predetermined location with relation to the box bottom 102, as loaded thereon.

A cross-frame or transverse wall structure at the rear of the cantilevered platform 104, upstands from the forward end portion of the base 101, and six diagonal brace members 127a, 127b, 127e, 1270, 127e and 1271, with rear, lower ends connected to the box bottom 102, have their upper ends connected to the wall structure or rear cross-frame 130 of the forward cantilevered section 103 at a spaced distance above the base 101, as best indicated in FIG. 9.

A cross-shaft 128, journalled in uprights 129a, 12%, FIG. 13, which upstand within the forward end of the box bottom 102, extends across the forward end of the box bottom 102, and has six pivot arms 108 mounted thereon, the axis of the crossshaft 128 being at the same distance above base level as the axes of the pivot pins 120 on which the lower ends of the pivot arms 109 are pivotally mounted. Each runner 123 of the upper hammer section 107a provides a lug 131 on the forward end thereof to receive therethrough a cross-shaft 129 on which the upper ends of the six pivot arms 109 are pivotally mounted. Noticeably the distance between pivot axes on the pivot arms 108 is the same as the distance between pivot axes on the pivot arms 109. Also the distance between the upper pivot axes 129, 121 is the same as the distance between the lower pivot axes 128, 120. Thus a pantagraph arrangement on each side of the forward portion of the hammer 101 insures that it can move with under crushing surface 110 substantially in the horizontal during its smashing or crushing action.

Details of hammer construction are shown in FIGS. and ll, the lower section 1071) being indicated as including a shaped rear end or nose 132 to channelize the rearward and downward movement of the upper rear portion of crushed metal contacted in hammer descent. Noticeably the opposed sides of the lower hammer 107b comprise rail guards 133a, 133b which extend downwardly below the level of the under side plate or crushing contact surface 110 of the hammer 107, thus to resist the tendency of parts of the crushed metal from working upwardly between hammer and side walls 113, 114.

Also, in order to channelize or form the uppermost crushed surface of the jnnked metal along the opposed upper corners of the mass, diagonally extending plates 134a, 1341) may be disposed with lower edges connected along the inner, lower edges of the rail guard plates 133a, 13312, and upper edges of the plates 134a, 1314b connected to the crushing plate or hammer under side surface 110. These elements 133a, 134a, and 133b, 1341; are indicated as extending for the full lengths of the respective left and right sides of the lower hammer section 107a.

As shown in FIGS. 9 and 10, plates 135a, 135b, 1350 and 135d fill in between the inner legs of the respective upright angles 115a and 115b, 1151; and 115e, 118a and 118b, and 119a and 1191;, on each side, to complete the side walls 113, 114. Gaps 136, 137 are thus provided between the uprights 1156', 118a and the uprights 118b, 119a, respectively, on each side, so that the lift prongs of fork lift trucks may be inserted just above the floor 116 of the box 102 to handle bodies to be crushed, and after crushing. Wells 138 and 139 are formed or de ressed in the floor 116 at spaced apart distance corresponding generally with the automobile wheel spacing apart. Also, upon first impact junked metal parts are crushed down into the wells 138, 139 and thus latch the automobile body in place against any further longitudinal displacement so that the remainder of impact following this initial fixing of the junked automobile, is directed entirely in vertical crushing. Also, since the wells 138, 139 extend all the way across the box bottom, air compressed by impact of hammer may escape sidewardly through these wells 138, 139, also cleanout can be accomplished sidewardly therefrom. Also, the runner 11715 on each side has recess 140 therein, FIG. 9, to receive the outer ends of the pivot pins 121 at the end of hammer drop.

Also, the opposed, pivoted arms 109 have holes 142 therein, so that a safety latch bar, inserted through such holes 142, may rest in the recesses 141 and thus serve as a safeguard in keeping the hammer 107 in upwardly latched position, as when an operator may be working in the box bottom 102. Also, noticeably in FIG. 10, bearings 143a, 1432: are provided on each outer side of the plate 135b, for the pivot shaft 120, and just inboard of the pivot arms 108 thereon. Additional features include soil anchors 144 on each corner of the base 101, comprising anchor plates 145 hinged upwardly on head pins 146 which extend transversely outwardly at spaced distances above the ground and from the side of the base 101. The anchor plates 145 extend rearwardly and downwardly over guide pins 147 which also extend outwardly from the side of the base 101 and to the rear of, and at a lower level than the head or hinge pins 146. Thus, as service would ordinarily tend to drive or slide the machine rearwardly along the ground 150 upon which rests the base 101, the anchor plates are driven into the ground to stop any further tendency toward rearward displacement.

Referring now in detail to FIGS. 12, 13 and 14, the upper hammer section 107a is shown as comprised of side runners 123 cross-connected forwardly by a heavy cross-bar 148, and cross-connected rearwardly thereof by cross-members 149. Also, as aforesaid, vertical upright members connect the upper and lower hammer sections 107a, 107b, as shown in FIG. 9; uprights 122a and 1221) also being indicated in FIG. 13 below the runners 123 and additionally an upright 122a being shown in FIG. 12. The lower hammer section 1117b is indicated in FIG. 13 as having a central, longitudinally extending chamber 151 down the middle thereof, as provided between two parallel extending, longitudinal members 152a, 1521), which may preferably consist of conventional channels, oppositely facing with webs outboard.

In FIG. 13 the space between the channels 152a, 15211, is shown uncovered, for purposes of clarity, but in'FIG. 12 this space is indicated as being closed over by strength memberplate 153, which extends from channel flange to channel flange, and which can be removably installed to permit removal to give access from above to service the cable 106 and other apparatus Within the chamber 151. As indicated in FIG. 12, an eye-bolt 154 has its shank extended rearwardly through a dead end plate 155 across the chamber 151 and a nut 156 is threaded onto the end of the shank of the eye-bolt 154 to bear on the rear face of the dead end plate 155 when the cable 106 is in tension. The rear end of a coil spring 157 is dead ended in the eyelet of the eye-bolt 154, and the forward end thereof is connected to a swivel 158 having the rear end of the cable 106 dead ended to the forward end of the said swivel 158.

The cable 106 extends through a stop washer 159 shown thereon in FIG. 12 just forwardly of the swivel 158, and thence the cable 106 extends through a bore 161 therefor through a stop plate which is located across the chamber 151 a short distance to the rear of the front end of the hammer section 1071;. From the stop plate 160 the cable 106 passes over the underside portion of a pulley 162 which is mounted on a shaft 162a which extends across the chamber 151 and is journalled in the webs of the opposed channels 152a, 1521) immediately adjacent the forward ends thereof and forwardly of the stop plate 160. From the underside of the pulley 162 the cable 106 extends upwardly and over a pulley 163 mounted on top the wall 130 and from thence to the drum 164 of a reel 165 supported upon the platform 104.

As shown more or less diagrammatically in FIG. 9, a prime mover, as a gasoline engine 166, is mounted forwardly on the platform 104. The engine 166 drives a pulley 167 which through belt drive 168 drives a larger diameter pulley 169 on a jack-shaft, not shown, trans mission means 170 on the same jack-shaft being indicated diagrammatically as drive-connected to brake and clutch means, not shown, but controlled by the brake lever 171 and clutch lever 172 indicated diagrammatically in FIG. 9. A manually operated lever 173 and lock 174 for the purpose of holding the hammer 107 in raised, locked position, and for then releasing the hammer 107 to descend, is also shown diagrammatically in FIG. 9.

Referring now to FIG. 12, the relative position of hammer 107 and associated apparatus indicate that the hammer 107 has reached the end of crushing stroke, and that the spring 157 has undergone its normal contraction to draw the cable 106 into the hammer chamber 151 for a distance found in practice to be best at approximately four feet. At this point all of the cable 106- has been 1 I wound off the drum 164 and the cable extends from its dead-end knot 175 in the drum 164, FIG. 15, to the groove of the pulley 163 with the shaft 176 of the drum 164 being in alignment with the cable as an extension from its point of tangency on the pulley 163. See cable 106 as shown in dotted lines in FIG. 15.

At this point the cable 106 closes an electric limit switch 177, shown diagrammatically on a bracket 180 which is carried by the upright frame or wall member 130. Closing of the limit switch 177 lets current pass to a conventional clutch moving solenoid 181, FIG. 13, which moves the clutch into en-clutched engine drive position, to transfer engine drive through conventional transmission 170, as indicated diagrammatically in FIG. 9, to drive the winch drum 164 counter-clockwise in FIGS. 9 and to wind the cable 106 back upon the drum 164.

After the innermost or rearmost four feet of cable, as aforesaid, has been drawn out of the hammer chamber 151, the stop washer 159 is brought in contact with the rear side of the stop plate 160, as the swivel 158 is drawn forwardly by the cable 106, and the spring 157 is stretched to fullest intended extent. The hammer 107 is now lifted as the drum 164 continues in counterclockwise drive. When the hammer 107 is completely raised, one of the members 108 (as the one which is shown in front of the cross-brace 1271: in FIG. 14), which carries a cross-plate 178 thereon, FIG. 12, is brought into contact with a limit switch 179 on the upright 130 thus to close the limit switch 179 so that a solenoid 182 actuates the application of brake band to the engine drive of the winch drum 164. Then the brake may be set by the lever 173 and locked by the lock mechanism to remain with hammer 107 in upper latched position until manually released.

The electrical diagram shown in FIG. 16 may best be followed through to understand the sequence of hammer raising, releasing, descent to smash, and re-raising. As the hammer 107 is raised, as hereinabove explained, the cross-plate 178 strikes the button of LS1 limit switch 179 to close a circuit which includes in series the brake solenoid SOL 182 and a manual push button release 183. The LS1 limit switch 179 being a double pole switch, it also closes a parallel circuit containing R1 relay 184 therein. When R1 relay 184 is energized it closes relay switch R1 (NO) in a circuit with R2 relay 185 and relay switch R3NC. When the latching R2 relay 185 is energized it closes relay switch R2 (NO) (in parallel with relay switch R1 (NO), and consequently opens a relay switch R2 (NC) in a circuit with relay switch R3 (NO), the clutch solenoid SOL181, and R4 186. Thus, under conditions aforesaid, with full cable on winch drum, the brake drum is applied by SOL 182 operation to brake winch drum rotation, the motor drive is de-clutched for free wheeling by SOL 181 operation, and the hammer 107, in fully raised position, may be latched as a safeguard by the application of the lever lock 174 carried by the manually operated lever 173, FIG. 9.

When another vehicle body may be in position on the smasher bed and ready to be compressed, the operator may then remove the lever lock 174, and press the button release 183 to break the circuit containing the brake solenoid SOL182 so that the winch drum may wheel free to let the cable 106 roll off the winch drum 164 follow ing the descent of the hammer 107. The spring 157 within the lower hammer section 107b tends to add momentum to the start of descent, as it becomes free, upon brake release, to contract for the first time since the end of the preceding hammer descent.

When the hammer 107 reaches the end of its descent (has compressed a vehicle body as much as it will compress) so that the cable 106 from the winch drum 164 reaches the dotted line position of FIG. 15, the LS2 limit switch 177 closes circuit to energize the R3 relay 186 is energized to open relay switch R3 (NC) thus breaking circuit through, and deenergizing R2 relay 185.

Also, as this R3 relay 186 opens relay switch R3 (NC), as a latching relay it closes relay switch R3 (NO), while the R2 relay 1 85, upon being deenergized, has opened relay switch 1R2 (NO) and closed relay switch R2 (NC). Thus the circuit containing relay switch R3 (NO), relay switch R2 (NC), clutch solenoid SOL 181 and R4 relay 187 is closed to energize R4, relay 187 to close relay switch R4 (NO).

The provision of R4 relay 187 and relay switch R4 (NO) insures that the clutch solenoid SOL 181 stays energized to keep the engine enclutched to drive the winch drum 164 after the hammer begins to rise. This need is obvious, since as the cable 106 (dotted position, FIG. 15) first begins to lift the hammer 107, it moves away from the LS2 limit switch 177 so that it can open. The circuit including relay switch R4 (NO), relay switch R2 (NC), clutch solenoid SOL 181 (energized) and R4 relay 1 87 (energized) thus continues closed until the hammer 107 is lifted all the way to uppermost position when the cross-plate 178 on a pivot arm 108 actuates the LS1 limit switch 179 to return conditions to the point hereinabove where tlu's description of operations started.

A form of the invention is shown in FIGS. 17-21, which may be termed a preferred form in that it provides semi-automatic mechanical elements for continued operation. A motor driven arrangement 200 is shown at least partially diagrammatically in FIG. 17, with a Diesel or gasoline engine driven motor 166a is indicated as acting through a transmission represented by the reference numerals 170a, 1701; applied respectively to a guarded transmission and machine gear box to transmit drive to a hoist drum 164a to pay out cable 106a. A brake lever 171 is shown diagrammatically with lower end rigidly connected to a horizontally extending rod or shaft 188 in journal bars 189a which extend from one of a pair of support runners 190a, 1901; mounted upon the journal providing members, not shown, for the winch drum 164a.

A lever 191 is rigidly connected to the left end of the rod or shaft 188, FIG. 17, and a connecting rod 191a on the outer, upper end of the lever 191 makes connection with a brake band 192 about the brake drum 193 of the winch drum 164a. Now, if the brake lever 171 is urged forwardly, (see arrow), as against the friction interposed by a friction quadrant, not shown in FIG. 17, but indicated by the quadrant 194, FIG. 20, then the lever 191 is swung downwardly (counterclockwise) so that the brake band 192 is applied to brake the drum flange or brake drum 193.

Considering FIG. 17 the clutch lever 172 has been urged forwardly, as per dotted line arrow, to pivot counterclockwise the rod or shaft 195 which is rigidly connected thereto, the shaft 195 being journalled in journals provided by journal bars 18% which are indicated as extending forwardly from the support runner 19%. This has lifted a connecting rod 196 shown as extending upwardly from the outer end of a lever 197 for upper end pivotal connection across the bifurcated right end of a bellcrank lever 198 with junction mounted for the bellcrank lever to pivot centrally upon a transverse pin indicated as extending horizontally from a support, as from the top face of the rearward support runner 1901;.

The upper end of the bellcrank lever 198 carries a fork 198a thereon to engage a flange 199a of a cone type clutch 199 with cone 19915 out of engagement within the drum flange 164b of the winch drum 164a with the clutch 199 in leftward position as shown in FIG. 17 and also in FIG. 18. Then if the clutch lever 172a is now moved rearwardly as indicated by the full line arrow in FIG. 17, the cone surface 199!) of the clutch 199 will be moved to the right and into internal engagement, not shown, within the drum flange 164b, as the clutch 19%, to which the clutch cone 19% is rigidly connected, is moved outwardly upon the drive shaft 176a, and into 13 driving connection therewith, as by cooperative keyway and spline or key means, not shown.

The lower end of the clutch lever 172 has a spring 201 shown as extending forwardly and upwardly therefrom, as will be described hereinbelow. Also a clutch lever setting rod 202 has its bifurcated forward end fitting 202a pivotally connected across the clutch lever 172 at a point above the spring 201 and below the clutch lever pivot shaft or axle 195. The operation of the rod 202 will be hereinbelow described.

Also in FIG. 17 a brake setting device 203 is indicated as providing a forward rod or rod portion 203a to bear against the rear face of the brake lever 188 above the brake lever pivot shaft or axle 188. This device is indicated as including a floor supported lost motion cylinder or housing 203!) and a rearwardly disposed rod or rod portion 2030. The operation of the brake setting device 203 will be explained in further detail hereinbelow in relation to description of FIGS. and 22.

Referring now to FIG. 18, the apparatus 205 for releasing the hammer -10.'7a to descend and crush a junked vehicle, then to be returned automatically to upwardly, releasably latched position, is shown as having released the hammer 107a for descent, and the hammer is just approaching the bottom of its stroke, or to lowermost crushing or compressing position. In this view most all of the cable 106a has been unreeled from the cable drum 164a and the position is being approached where the cable 106a will extend, as all unreeled, along a line between the drum shaft 176a (on which the drum 164a has been free-wheeling), the cable dead end notch 175a, and the groove of the pulley 163a.

As shown, the cable 106a is still spaced from contact with a contact plate or disk 204 on the forward end of a pawl lift rod 206 which extends horizontally through mounting straps 207 on opposite ends of a vertically disposed mounting plate 208 carried by a frame post or upright 130a, which upstands above the platform 104a. The rod 206 carries a wedge 209 which extends through a cam slot 211, (FIG. 19), provided by a pawl 210 shown in FIG. 18 as having longitudinally (vertically) spaced apart vertical slots 212 therein, with machine bolts 213 extending through the upper ends of the slots 212 and into the upright 130a, whereby the pawl 210 is mounted on the upright 130a and in relation to the wedge rod 206.

In FIGS. 18 and 19 the pawl 210 is shown as having its lower end 210a tapered to a forwardly provided point to engage with ratchet teeth provided in a ratchet 214 which is disposed to slide longitudinally, or from front to rear, in a guide slide 215 mounted at an appropriate elevation on the upright 130a below the pawl mounting machine bolts 213. The ratchet 214 has upwardly facing teeth 216 therein to be selectively engaged by the pawl tooth 210a in accordance with longitudinal, horizontal movement of the ratchet 214.

Ratchet movement is effected by a bellcrank lever 217 having a slot 218 in its upper leg 217a for engagement with a cross-pin 219 which extends transversely horizontally from the forward end 220 of the ratchet 214. Such bellcrank lever 217 pivots centrally upon a cross-pin 221 which extends transversely, horizontally from the upright 130a, and the lower leg 217b is pivotally connected to the bifurcated rear end 202b of the clutch lever setting rod 202 as introduced with description of FIG. 17. In FIG. 18 the aforesaid shaft or axle 195 to which the clutch lever 172a is rigidly connected, is indicated as journalled in a quadrant bracket 222 in addition to the journal bars 18% shown in FIG. 17. Also in FIG. 18, the spring 201, introduced in description of FIG. 17, is shown having its forward end connected to a bracket 223 provided by the platform 104, and stretched by the clutch lever 172a in this clutch disengaged position.

Referring now to FIG. 19, the hammer has reached the bottom of its descent and all the cable 106:: has been paid out, and the dead center cable position has been reached, with shaft 176a, dead end notch a, and groove of pulley 163a in alignment. Th cable has thus contacted the foot or disk plate 204 on the forward end of the wedge or pawl rod 206 to mov it to the right. As a consequence the wedge 209 has lifted the pawl 210 from successive ratchet tooth contact by lifting the pawl 210 with relation to the machine bolts 213 within its slots 212, the cam slot in the pawl 210 being engaged by the tapered wedge 209 at areas higher in elevation. As this occurs the aforesaid spring 201 may contract and draw the lower end of the clutch lever 172a forwardly as the upper end of the clutch lever 172a is urged rearwardly as indicated by full line arrow in FIG. 19.

As hereinabove described, as the clutch lever 172a has had its upper end urged rearwardly by the contraction of the spring 201, clockwise rotation of the clutch lever cross shaft 195 draws the right leg of the bellcrank lever 198 downwardly, so that the fork 198a urges the clutch flange 199a to the right. This brings the surface of the clutch cone 19912 within the drum flanges 16% into engagement with the inner, drive transmitting surface of the drum flange 164b, not shown, as the clutch flange 199a is forced into drive establishing engagement, not shown, with the winch drum shaft 176a, as driven from the gear box 170b, in turn driven by the transmission 170a from the motor 166a.

The winch drum 164a is now driven in direction to raise the hammer and wind up the cable 106a on the drum. When most of the cable has thus been wound up, the hammer approaches upper or raised position and a forward pivot arm 108a approaches the vertical near the upright 130a. Finally, the pivot arm first strikes the ratchet 214 to urge it to the left so that the pawl 210 descends into ratchet tooth engagement, as in FIG. 18, whereas the pawl lift or widge carrying rod 206 is also contacted by the aforesaid pivot arm 108a and moved to the left to the relative position indicated in FIG. 18. Obviously, as the cable 106a has been wound up it has moved to the left with relation to the contact plate or disk 204 on the left end of the rod 206, and now, when the hammer is drawn back up to upper position, the disk plate 204 is returned to the same proximity to the cable 106a shown in FIG. 18.

Heretofore the description of operation has related generally to the clutch setting operation and the brake lever 171a and its associated elements have been omitted from FIGS. 18 and 19 for purposes of clarity. As shown in FIG. 20, the brake lever 171a has been moved to brake setting position as indicated by the dotted line arrow, also shown in FIG. 17. The aforesaid brake lever cross-shaft 188, introduced in description of FIG. 17 as being journalled in journal bars 18%, is also indicated in FIG. 20 as being journalled in a brake quadrant bracket 194 supported by the platform 104a, and by the reference it may be established that the support runners a, 190k must also be supported substantially at the elevation of the platform 104a. Also, as heretofore introduced in description of FIG. 17, the brake setting device 203 comprises a rod portion 203a forwardly to contact the brake lever 171 above the cross-shaft 188, a cylinder or sleeve assembly 203b supported by an upright stand 224 above the platform 104a, and a rear rod portion 2030 which terminates rearwardly in a bearing plate or disc to be contacted by a pivot arm 108a of the hammer when it is in fully lifted position. A guide clamp or bracket 226 at forward and rear face of the upright or frame member 130a receives the rear rod portion 203a therethrough and a spring 227 surrounds the rear end portion of the rod portion 2030 to bear forwardly against the upright 130a and rearwardly against the bearing plate or disc 225.

The sleeve assmbly 203b, as best shown in detail in FIG. 21 includes a cylindrical body member 228a, which is centrally aflixed to the top of the stand 224, not shown. The cylindrical body member 228a has the rear end of the forward rod portion 203a connected into its closed forward end 2281).

The sleeve assembly 2031) has the flange 2280 on the forward end of the rear rod portion 2030 insertable into the rear end of the cylindrical body 228a to bear on the rear of a biasing spring 228d to urge its forward end against the inner face of the forward sleeve closure 228k. A rear closure cap 228e is insertable over or around the rear rod portion 203s and threadable upon the cylindrical body member 228a to complete the sleeve assembly 2G3b. There is thus provided a lost motion arrangement, to be hereinbelow described, between brake lever 171a forwardly, and pivot arm 108a of the hammer 107a.

As the hammer 107:: has ascended, the aforesaid pivot arm 108a, which carries a transversely horizontally extending anchor pin 229, approaches a latch member 239 in the form of a bellcrank lever wtih rearward arm 230a having specially formed teeth 2300 comprising the under side thereof. The bellcrank latch member 230 pivots centrally upon a transversely horizontally extending pivot pin 231 on the upright 103a, and a spring 232 having lower end connected to the forward upper corner of the forward bellcrank lever arm 230b, and upper end connected thereabove to the upright 130a, thus to bias the rear bellcrank lever arm 230a downwardly.

A connection fitting 233a on the upper end of a flexible cable 233 makes connection to the under side of the forward arm 23% of the bellcrank lever 230 and extends rearwardly and downwardly over an upper pulley 234a mounted on the upright member 130a, and on the rear side of a lower pulley 23412 mounted therebelow on the platform 104a. Thence the flexible cable 233 extends to the lower leg 235a of a bellcrank lever 235 with central pivot 2350 just above the level of the platform floor 130a and with the upper leg 2351; of the bellcrank lever 235 senving as a foot treadle.

It thus occurs that hammer pivot arm contact, as the hammer 107a is returned to fully raised position, acts upon one means that automatically tie-clutches the winch drum 164a from motor drive, FIGS. 18 and 19; acts upon another means independently to set the brake band 192 tightly against the brake drum 193, FIG. 20; and acts upon a third means independently to latch the hammer 107:: in upper position, FIG. 20.

The lost motion assembly 2031) serves one purpose of safeguarding against breakage, which otherwise might occur in case of hammer lift over-travel with a rigid brake setting rod assembly, the breakage thus tending to occur in the chain of mechanism from and including brake band, and elements therefrom back to the pad or plate 225 which immediately contacts hammer pivot arm. Also, the provision of resilient means in the brake setting rod assembly 230 buffs over-travel of the anchor pin 229, which tends to ride upon the rear face of a tooth 230a forwardly of the notch between teeth, but for the rearward urging of the biasing spring 228d, FIG. 21, which returns the hammer 107a from any over-travel to tooth notch engagement of latch lever 230 with anchor pin 229.

Noticeably in the clutch lever quadrant 222 no teeth are indicated and the clutch lever is controlled by physical attachment to the clutch lever setting rod 202 which starts the chain of elements ending in the clutch cone 1991) being latched in surface disengagement with the inner surface, not shown, of the drum clutch 164b, this being accomplished at the end of the aforesaid chain by the engagement of the pawl tooth 210a with a ratchet tooth 216. On the other hand, the brake lever quadrant 194, is shown as being provided with a toothed quadrant 194a by the dotted line arc, FIG. 20.

In order to set the hammer 107a back in crushing operation, the operator first puts his foot on the foot treadle 2351) provided by the bellcrank lever 235. As the hammer 10711 is not latched upwardly by a rigid brake lever setting rod, the bellcrank lever arm 230a can be pivoted upwardly by the downward travel of the flexible cable 233 as the mass of the hammer 107a does not enter into holding the anchor pin 229 in tooth engagement, as this effect is counter-balanced by virtue of the yieldability of the biasing spring 228d in the brake lever rod sleeve assembly 20Gb.

With the operators foot pressing down the foot treadle 2351), he now manually urges the brake lever 171a rearwardly toward the dotted line position shown in FIG. 20. Normally, with conventional lever pawl, quadrant tooth engagement, difiiculty would be experienced in urging the brake lever 171a rearwardly out of brake quadrant tooth engagement, if opposed by a rigid brake setting rod disposed between the brake lever 171a and hammer 107a. However, with the lost-motion sleeve assembly 2031) interposed in the brake setting rod assembly 203, the operator can disengage the brake lever pawl from the tooth it has been engaged with so that the brake band 192 can release the brake drum 193 enough to let the winch drum 164a start free-wheeling. Also, at this point, the momentum of the mass of the hammer 107a, in descent, will be abetted by the contraction of the hammer spring 157, FIG. 12, as at this instant the spring 157 is relieved of the force that has been holding it with washer 159 against the rear face of the stop plate 160.

Referring now to the form of the invention shown in FIGS. 13, 15 and 16, the current, indicated as volts, AC, may also be supplied by DC. voltage. Also, all of the apparatus shown in FIG. 16, including the manually operated master switch 236, and excluding limit switches and solenoids, may be provided in a panel, not indicated in the drawings, but disposed at any preferred location.

Although one form of the invention shows the hammer lift and release and apparatus of electrical type, and another form shows hammer lift and release all by mechanical means, the invention is not thus limited, and hydraulic systems, pneumatic systems, and various combinations of electrical, mechanical, hydraulic, and pneumatic systems may be employed, with the claims thereto being illustrative only.

I claim:

1. A junked metal compressing smasher comprising a base with a forward platform, side walls, and a rear stop wall, a hammer to fall within said walls, pivot means transversely across the forward portion of said base adjacent said platform, pivot arms interconnecting said pivot means and said hammer, hammer lift means on said platform, cable means continuously connected to said hammer during descent and return to upper position, and cooperative means operable in association with said cable means and said hammer lift means to return said hammer to lifted position after each descent to smash junked metal disposed on said base, pulley means being provided in said hammer adjacent the bottom thereof and on said platform and said cable means extending under said pulley means in the hammer and over said pulley means on the platform and having one end dead-ended on said hammer lift means and the other end dead-ended on said hammer.

2. A junked metal compressing smasher as claimed in claim 1 in which the end of said cable means dead-ended to said hammer comprises a spring.

3. A junked metal compressing smasher as claimed in claim 1 in which said hammer lift means comprises a reel drum on which said cable is wound, and engine means for driving the reel drum, said engine drive being de-clutched as said hammer is lifted, and said smasher additionally including a releasable brake to hold said harnmer in upwardly latched position.

4. A junked metal compressing smasher as claimed in claim 1 in which said hammer includes a selectively movable counterweight to locate center of smashing impact.

5. A junked metal compressing smasher comprising a base with a forward platform, side Walls, and a rear stop wall, a hammer to fall within said walls, pantograph type support means for said hammer including forward support arms transversely aligned across said base with lower pivots on said base adjacent said platform and rear support arms transversely aligned across said base with lower pivots on said base at predetermined distance rearwardly of the aforesaid lower pivots, said support arms having upper pivots at respective distances from said lower pivots and said upper pivots being transversely aligned across the front of and connected to said hammer and across said hammer at said predetermined distance rearwardly of said front alignment, whereby said hammer presents a substantially continuously horizontal plane of smashing contact in descent, said smasher including hammer lift means on said platform, cable means with one end continuously dead-ended to said hammer and the other end continuously dead-ended to said hammer lift means, and co-operative means operable in association with said cable means and said hammer lift means to return said hammer to an upper latched position after each metal smashing descent, latch means operative upon hammer ascent to latch said hammer in raised position and operable to trigger descent of said hammer.

6. A junked metal compressing smasher as claimed in claim 5 in which said side walls are grooved to receive upper rear pivot arm pivots at end of smashing stroke.

7. A junked metal compressing smasher as claimed in claim 5 in which said co-operative means includes limit switch means.

'8. A junked metal compressing smasher as claimed in claim 5 in which said co-operative means includes lost motion, yieldable means.

9. A junked metal compressing smasher as claimed in claim 5 in which said cooperative means includes latch means actuated upon ascent of said hammer to lifted position to engage said hammer in upwardly, releasably latched position, and manually operable to release said hammer for descent.

10. A junked metal compressing smasher as claimed in claim 5 in which said cooperative means includes a winch drum with brake band applied by brake lever operation to brake said winch drum in cable wound up hammer uplifted position, said winch drum being set free-wheeling by manual operation of brake lever to pay out cable for hammer descent.

11. A junked metal compressing smasher as claimed in claim 5 in which said cooperative means includes toothed latch mechanism manually operable to release hammer for descent.

References Cited UNITED STATES PATENTS 937,436 10/1909 Haag 100-265 X 2,986,992 6/1961 Patros et al 100-218 2,997,942 8/1961 Dunham et a1. 100-265 X 3,036,516 5/1962 Purcell 100-265 X 3,237,554 3/1966 Davis 100-218 BILLY J. WILHITE, Primary Examiner US. Cl. X.R. 

